CN110552633A

CN110552633A - Threaded connection

Info

Publication number: CN110552633A
Application number: CN201910753418.2A
Authority: CN
Inventors: 默勒·E·埃文斯; 耶伦·斯泰恩·朱莉安·万维滕贝格
Original assignee: ArcelorMittal Tubular Products Lubembourg SA
Current assignee: ArcelorMittal Tubular Products Lubembourg SA
Priority date: 2015-02-19
Filing date: 2016-02-12
Publication date: 2019-12-10
Anticipated expiration: 2036-02-12
Also published as: US20160245433A1; KR20180013841A; WO2016132232A1; CN107407447A; EP3259436B1; US10612700B2; US10006569B2; EP3259436A1; MX2017010518A; CA2977306C; JP6689888B2; CN110552633B; CN107407447B; RU2681152C1; US20200200303A1; MX2021000833A; CA2977306A1; JP2018505368A; US11614184B2; BR112017017714B1

Abstract

A threaded connection includes a first tubular (10) having a pin (20) with a pin thread (22), a circumferential concave outer pin surface including a pin sealing surface (24), and a pin torque shoulder at a free end (26). The second pipe (100) has a socket (120) with a socket thread (122) for interacting with the pin thread, a circumferential inner socket surface, and a socket torque shoulder (126). The inner shroud surface has a radially inwardly extending shroud sealing surface (124), and the pin sealing surface (24) contacts the shroud sealing surface (124) to define a seal. The seal is spaced from the free end when the pin torque shoulder contacts the box torque shoulder.

Description

Threaded connection

This application is a divisional application filed on 2016, 12.2.2016 under the name of 201680010026.1 (International application No. PCT/IB2016/000396), entitled "threaded connection for pipes such as oil and gas pipelines".

Technical Field

the present invention relates to threaded pipes and connectors for such pipes as used in the oil and gas industry. For example, the pipe may have an end with a pin that fits into the socket at one end of the connector, the pipe and connector being connected by threads. The connector may have a second socket for another pipe with another pin so that the pipe and the other pipe are connected via the connector.

background

Us patent No.4,623,173 describes a threaded joint coupling for petroleum pipelines. The main seal portion is provided with a seal portion axially protruding at an end of the external thread and a seal portion tapered at an inner side of the internal thread, and an end point of the external thread is butted against an end portion of a stopper formed at the inner side of the internal thread.

U.S. patent No.7,334,821 describes a threaded tubular connection having an externally threaded member and an internally threaded member. The externally threaded element has an external thread and a free end with a non-threaded lip between the thread and the free end. The female threaded element has an internal tapered female thread and a non-threaded portion between the female thread and the lug. The internally threaded element comprises an annular axial abutment surface. After the external thread is fully assembled in the internal thread, the free end bears against an annular axial abutment surface, the other bearing surfaces radially interfering with this annular axial abutment surface and being under metal-to-metal contact pressure to constitute metal-to-metal sealing surfaces.

Thus, in the' 821 patent, another axial abutment surface is formed on the front surface of the free end of the male threaded element, and a single lip sealing surface is disposed on the lip at an axial distance from the end of the thread. The lip includes an appendage between the distal axial abutment surface and the single lip sealing surface having an outer peripheral surface facing a different internally threaded member than the lip sealing surface.

Disclosure of Invention

During the make-up of a connection between a threaded pipe with a pin, such as a pipe, and a threaded pipe with a box, such as a connector, the following sequence occurs: (1) the pin on the pipe is inserted into the connector until the thread tops come into contact; (2) the pin is then screwed into the socket until the pin sealing surface just contacts the socket sealing surface to define a position known as "hand-tightening"; (3) the pin is screwed further into the socket until the end of the pin, the so-called torque shoulder, just contacts a corresponding torque shoulder on the socket to define a position known as "shoulder tightened", this additional rotation from the hand tightened position to the shoulder tightened position causing an interference fit between the pin sealing surface and the socket sealing surface; and (4) the pin is further tightened to generate additional torque, thereby defining a final assembly position known as "power tightening".

the distance between the pin torque shoulder and the box torque shoulder when the connection is in the hand-tightened position is referred to as the "gap," which is eliminated once the shoulder-tightened position is reached. Larger spacings can be problematic: as the spacing is eliminated, the sealing surfaces contact. The large rotation caused by the large spacing may cause wear of the sealing surfaces, thus compromising the seal.

it may also be desirable for the maximum contact stress of the pin and socket at the seal to be further away from the end of the pin to improve the seal.

It is an object of the present invention to provide a seal having a point of maximum contact stress well away from the end of the pin while limiting the amount of separation. An alternative or additional object is to provide a connection which is easy to manufacture.

a threaded connection includes a first tube having a pin with a pin thread, a circumferential concave outer pin surface, and a pin torque shoulder at a free end. The concave outer pin surface includes a pin sealing surface and a continuous extension from the pin sealing surface to the pin torque shoulder. The second tube has a sleeve with a sleeve thread, a circumferential inner sleeve surface with a radially inwardly extending sleeve sealing surface, and a sleeve torque shoulder. The pin sealing surface contacts the box sealing surface to define a seal spaced from the free end when the pin torque shoulder and the box torque shoulder are in contact, the continuous extension continuing from the seal to the pin torque shoulder.

The continuous concave outer pin surface thus advantageously provides a single surface along which the inner jacket surface can interact with to form the seal, and the seal can be formed with maximum contact stress away from the end with the smaller spacing. Wear can be reduced while still providing a good seal. Furthermore, the required precision of the different surfaces of the prior art can be avoided and manufacturing and assembly can be simplified.

The following further features of the threaded connection may have advantages alone or in combination with other further features:

The pin sealing surface extends radially inward toward the free end, and the extension curves radially outward at the free end;

the cross-section of the pin torque shoulder and/or the box torque shoulder is V-shaped;

the pin threads are double-start threads;

The first tube is a pipe and the second tube is a connector having a second socket similar to the socket on the second end;

A line tangent to the box seal surface radius and the pin seal surface radius at a point of maximum contact stress at power fastening assembly forms an angle of 5 degrees to 15 degrees with the longitudinal axis of the first and second tubes, and most preferably the angle is 10 degrees; and

The distance from the end of the pin (at the pin surface) to the point of maximum stress contact of the seal is preferably in the range of 0.5 inches to 1.5 inches, most preferably 1 inch.

the present invention also provides a method for assembling a threaded connection having: a first tube having a pin with a pin thread, a circumferential concave outer pin surface comprising a pin sealing surface and a continuous extension from the pin sealing surface to the pin torque shoulder, and a pin torque shoulder at a free end; and a second pipe having a socket with a socket thread, a circumferential inner socket surface with a radially inwardly extending socket sealing surface, and a socket torque shoulder. The method comprises the following steps: inserting the first pipe into the second pipe until the pin threads and the box threads contact; threading the first pipe into the second pipe via the pin threads and the box threads until the outer pin surface contacts the inner box surface and the pin torque shoulder is spaced a spaced distance from the box torque shoulder; threading the first tube further into the second tube until the pin torque shoulder just contacts the box torque shoulder in the shoulder tightened position, the pin sealing surface contacting the box sealing surface to define a seal, the seal spaced from the free end in the shoulder tightened position; and after the shoulder-securing position, screwing the first tube further into the second tube to define a final assembly position.

The following further features of the method may have advantages alone or in combination with other further features:

the number of turns during the further screwing step is less than 0.5,

The separation distance is between 0.02 inches and 0.25 inches;

the pin threads are double-start threads; and

the first pipe is a pipe and the second pipe is a connector having a second socket similar to the socket on the second end.

Drawings

The drawings depict exemplary embodiments of the present invention.

FIG. 1 illustrates one embodiment of the present invention in which a pin of a petroleum pipeline is inserted into a socket of a connector;

fig. 2 shows that in a second stage of assembly: a connection with the petroleum pipe 10 and the connector 100 in a manually tightened position;

Fig. 3 shows a third stage of assembly: fastening the shoulder;

FIG. 4 shows a graph of the change in torque applied to a connection during make-up of the connection;

FIG. 5 shows an enlarged view of the sealing area of FIG. 3;

FIG. 6 schematically illustrates the extension of the pin seal radius and the box seal radius;

FIG. 7 shows a detail of the torque shoulder of the embodiment of FIGS. 1-6; and is

fig. 8 shows a second embodiment of the present invention.

Detailed Description

Fig. 1 shows the petroleum pipe 10 and connector 100 in a first stage of insertion position. The petroleum pipeline 10 has a pin 20, the pin 20 having a threaded section 22, a pin sealing surface 24, and a torque shoulder 26 at the free end. Connector 100 has two sleeves 120, 220. Each shroud has a threaded section 122, a shroud sealing surface 124, and a torque shoulder 126 on a radially inward protrusion 150. The connector 100 has two free ends 102 and 202.

Fig. 2 shows that in a second stage of assembly: the connection with the petroleum pipe 10 and the connector 100 in the manually tightened position, where the pin sealing surface 24 and the box sealing surface 124 just come into contact. In the manual tightening position, a space S exists between pin torque shoulder 26 and box torque shoulder 126. In this embodiment, the spacing S is about 0.060 inches, although the spacing S may vary greatly due to the designed seal interference and seal angle.

FIG. 3 shows a third stage of assembly when the torque shoulder 26, 126 is just touching but before any force from the additional torque is applied to the torque shoulder 26, 126: and the shoulders are fastened. Therefore, the spacing S is preferably eliminated in less than 0.5 rotations. In the shoulder-tightened position, the sealing surfaces 24, 124 have been forced together by threading the pin into the sleeve until the torque shoulders 26 and 126 contact. Due to the relative angles of the sealing surfaces 24, 124, the surfaces have been forced radially apart by a certain amount of sealing interference designed into the connection to create sufficient contact pressure to form a leak-proof seal. There is a distance S1 in the radial direction between the surface BS and the end of the pin 20.

the fourth and final stages of assembly are dynamic fastening. During the power-on phase, additional torque is applied to the torque shoulders 26, 126, but very little additional rotation occurs, about 0.01 revolutions in the illustrated embodiment. Preferably, the threads 22 are double start threads so that wear is further reduced. Because the additional rotation that occurs is very small, the connection appears to be approximately in the shoulder-tightened position as shown in FIG. 3.

Fig. 4 shows a graph of the variation of the torque applied to the connection during the makeup of the connection. At the zero-turn position, pin 20 has been inserted into sleeve 120, as shown in FIG. 1. At this point, pin 20 is merely placed in sleeve 120 and no rotation is applied. After the connector is inserted, the pin 20 is screwed into the socket 120. In the embodiment shown, about 8 turns of screwing are required before sealing contact. During these initial turns, there is no torque build up due to the free running of the threads during this period. At about 8 revolutions, the sealing surfaces 24, 124 are in contact at the manually tightened position. Once the sealing surfaces 24, 124 are in contact, torque begins to build up rapidly. Torque build-up is caused by the sealing surfaces 24, 124 being wedged together. The amount of torque build-up is a function of the pin and box member friction, stiffness, amount of thread interference that may be present, and amount of interference in the seal around the seal area. The torque continues to increase at a generally constant rate until the shoulders 26, 126 come into contact. Once the shoulders 26, 126 are in contact, additional torque is applied until a predetermined power tightening make-up torque is reached. After a very small additional rotational contact of the shoulder with the connection, the torque builds up very rapidly, wherein the required final make-up torque can be reached with only about 0.01 turn. The final make-up torque may be set using a torque meter or torque program of the power tong.

FIG. 5 shows an enlarged view of the sealing area of FIG. 3, wherein the pin seal radius PSR and the box seal radius BSR are shown. The radius of the shroud sealing surface in this embodiment is 1.63826 inches and the radius of the pin sealing surface is 4.75 inches. The angle of the line tangent to the sealing surface radius at the point of maximum contact stress 324 at power fastening assembly is about 10 degrees, and in an advantageous embodiment the angle may vary between 5 and 15 degrees. This angle affects the seal during axial loading and bending, and also affects the wear resistance of the seal during assembly. The length from the end E of the pin (at the pin surface) to the point of maximum stress contact of the seal is most preferably about 1.0 inch. The length is preferably in the range of 0.5 inches to 1.5 inches. When the length is less than 0.5 inches, the seal contact stress begins to decrease, and when the length exceeds 1.5 inches, there is little additional effect on the seal contact.

together, points 324 and E and the distance between them define pin seal radius PSR. The size of the pin radius is primarily defined by the geometry of the end of the pin. It should also be noted that the sealing contact is not one point, but is distributed over a certain length. In the above discussion, the sealing contact point is the maximum stress contact point, where the two contact arc surfaces are located approximately at the center of the contact length.

The shroud seal radius in this design was 1.63826 inches. The shroud seal radius is ultimately determined by the desired contact stress distribution between the two sealing surfaces.

The seal contact stress distribution of a connection is generally a function of the following parameters:

The rigidity of the pin;

The stiffness of the pipe sleeve;

Interference between the two sealing surfaces; and

the shape of the sealing surface.

In the present invention, if the pin radius is made larger or the box radius is made smaller, and if the rest of the connection geometry remains approximately the same, the contact length decreases and the peak contact stress increases. While increasing the peak contact stress increases the sealing capability of the connection, it also increases the chance of seal wear during make-up, which is undesirable. Conversely, reducing the peak contact stress reduces the sealing capability of the connection, but this reduces the likelihood of seal wear during make-up, which is desirable. Therefore, balance must be maintained in order to form a seal that can seal without wearing during assembly. Since the pin seal is primarily determined by the pin geometry, the shroud seal radius should be designed to achieve the optimum contact stress distribution for a given pin seal radius. Since the coupling is designed for pipes of different wall thicknesses, the shroud seal radius is adjusted to maintain the optimum seal design criteria.

Fig. 5 shows a small circular area at the end E of the pin. The circular area connects the pin seal radius PSR to the torque shoulder surface 26. This area can simply be a chamfered or broken edge. Sharp edges are undesirable because burrs can form on sharp edges and become a safety issue for personnel inspecting the pin, and the burrs can break off during assembly and become trapped between the sealing surfaces and compromise the seal.

FIG. 6 schematically illustrates the extension of the pin seal radius PSR and the box seal radius BSR. These extensions may vary considerably, in particular the extension over the pipe sleeve, without affecting the invention. The present invention shows the radius of the socket tangent to the straight counterbore CB. The shroud seal radius may continue to intersect the counterbore at a sharp corner or at a blend between the radius and the counterbore. In this example, the pin radius produced angle PA is 16.29 degrees and the socket produced angle BA is 17.95 degrees. The location of the center point of the radius is not particularly important and is not shown correctly in these schematic diagrams. The schematic diagram in fig. 6, although fairly accurate, is for illustration purposes only.

As shown in fig. 7, in the embodiment of fig. 1-5, the torque shoulder is V-shaped. The V-shaped torque shoulder prevents the pin from being driven up into the socket corner by holding the pin in place. The bottom of the V-shaped shoulder also serves the purpose of preventing externally applied pressure from forcing the pin inwardly and breaking the seal. The V-shaped shoulder thus serves to hold the shoulder against movement in either a radially inward or radially outward direction. The upper and lower portions of the V-shaped shoulder are at an angle of 15 degrees relative to an axis perpendicular to the pipe. The angle may vary significantly (perhaps 5 to 30 degrees) and the angle of both the socket portion and the pin portion need not be equal. Furthermore, the place where the two portions meet need not be in the center of the shoulder as shown. The lower portion may be longer, and in many designs the lower portion is longer.

FIG. 8 shows a less preferred embodiment of the present invention without a V-shaped torque shoulder, with pin torque shoulder 326 angled inward to contact box torque shoulder 426.

Claims

1. A threaded connection, comprising:

A first tube having a pin with a pin thread, a circumferential concave outer pin surface comprising a pin sealing surface, and a pin torque shoulder at a free end; and

A second pipe having a box with box threads for interacting with the pin threads, a circumferential inner box surface having a radially inwardly extending box sealing surface, and a box torque shoulder, the pin sealing surface contacting the box sealing surface to define a seal spaced from the free end when the pin torque shoulder and the box torque shoulder are in contact.

2. A threaded connection, comprising:

a first tube having a pin with a pin thread, a circumferential concave outer pin surface comprising a pin sealing surface, and a pin torque shoulder at a free end, the pin sealing surface of the pin being axially spaced from the pin torque shoulder of the pin; and

A second pipe having a box with box threads for interacting with the pin threads, a circumferential inner box surface having a radially inwardly extending box sealing surface, and a box torque shoulder, the pin sealing surface contacting the box sealing surface to define a seal spaced from the free end when the pin torque shoulder and the box torque shoulder are in contact, wherein a gap is formed between the pin and the box between the seal and the pin torque shoulder.

3. A threaded connection, comprising:

A second pipe having a box with box threads for interacting with the pin threads, a circumferential inner box surface having a radially inwardly extending box sealing surface, and a box torque shoulder, the pin sealing surface contacting the box sealing surface to define a seal spaced from the free end when the pin torque shoulder and the box torque shoulder are in contact, wherein a pin sealing surface radius of the pin sealing surface is greater than a box sealing surface radius of the box sealing surface.

4. A threaded connection, comprising:

a first tube having a pin with a pin thread, a circumferential concave outer pin surface, and a pin torque shoulder at a free end, the concave outer pin surface including a concave pin sealing surface and a continuous extension from the pin sealing surface to the pin torque shoulder; and

A second pipe having a box with a box thread for interacting with the pin thread, a circumferential inner box surface having a radially inwardly extending box sealing surface, and a box torque shoulder, the pin sealing surface contacting the box sealing surface to define a seal spaced from the free end when the pin torque shoulder and the box torque shoulder are in contact, the continuous extension continuing from the seal to the pin torque shoulder.

5. A threaded connection, comprising:

A first tube having a pin with a pin thread, a circumferential concave outer pin surface, and a pin torque shoulder at a free end, the concave outer pin surface including a pin sealing surface and a continuous extension from the pin sealing surface to the pin torque shoulder; and

A second pipe having a box with box threads for interacting with the pin threads, a circumferential inner box surface having a radially inwardly extending box sealing surface, and a box torque shoulder, the pin sealing surface contacting the box sealing surface to define a seal spaced from the free end when the pin torque shoulder and the box torque shoulder are in contact, the continuous extension continuing from the seal to the pin torque shoulder,

the pin sealing surface is concave and the box sealing surface is convex at the seal, the continuous extension being continuous with and extending from the concave pin sealing surface to the pin torque shoulder.

6. a threaded connection, comprising:

a second pipe having a box with box threads for interacting with the pin threads, a circumferential inner box surface having a radially inwardly extending box sealing surface, and a box torque shoulder, the pin sealing surface contacting the box sealing surface to define a seal spaced from the free end when the pin torque shoulder and the box torque shoulder are in contact, the continuous extension continuing from the seal to the pin torque shoulder, the pin sealing surface being concave and extending radially inwardly toward the free end.

7. the threaded connection as recited in claim 1 wherein the box sealing surface is a convex surface having a box sealing radius of curvature that is less than a pin sealing surface radius of curvature.

8. The threaded connection as recited in claim 5 wherein the box sealing surface has a box sealing radius of curvature that is less than a pin sealing radius of curvature.

9. a threaded connection according to any one of claims 1 to 3, wherein the pin sealing surface extends radially inward toward the free end, and wherein the pin includes a continuous extension on the pin between the pin sealing surface and the pin torque shoulder, wherein the continuous extension curves radially outward at the free end.

10. A threaded connection according to any one of claims 4 to 6, in which the pin sealing surface extends radially inwards towards the free end, while the extension is curved radially outwards at the free end.

11. a threaded connection according to any one of the preceding claims, in which the circumferential concave outer pin surface is a single circumferential annular concave outer pin surface.

12. The threaded connection as recited in any of the preceding claims wherein at least one of the pin torque shoulder and the box torque shoulder is V-shaped in cross-section.

13. A threaded connection according to any one of the preceding claims, in which the first pipe is a pipe and the second pipe is a connector having a second socket similar to the socket on the second end.

14. A threaded connection according to any one of the preceding claims, in which a line tangent to the box and pin seal surface radii at the point of maximum contact stress at power fastening make-up forms an angle of 5 to 15 degrees with the longitudinal axis of the first and second pipes.

15. A threaded connection according to any one of the preceding claims, in which the distance from the end of the pin to the point of maximum stress contact of the seal is in the range 0.5 to 1.5 inches.

16. The threaded connection as recited in claim 15 wherein said distance from said end of said pin to a seal maximum stress contact point is about 1 inch.

17. The threaded connection as recited in any of the preceding claims wherein in a manual makeup position, the pin and box sealing surfaces just come into contact and there is a space between the pin and box torque shoulders.

18. the threaded connection of claim 17, wherein the spacing is about 0.060 inches.

19. The threaded connection as recited in any of the preceding claims wherein in the shoulder tightened position, the pin and box sealing surfaces contact each other and the pin and box torque shoulders contact each other with no space between the pin and box torque shoulders.

20. a threaded connection according to any one of the preceding claims, in which, in the shouldered tightened position, there is a sealing interference between the free end of the pin and a portion of the inner box surface.

21. The threaded connection as recited in claim 12 wherein the upper and lower portions of the V-shaped cross-section are between 5 and 30 degrees with respect to a line perpendicular to the axis of the threaded connection.

22. A threaded connection according to any one of claims 4 to 6, in which the continuous extension is curved radially outwards at the free end.

23. A threaded connection according to any one of claims 4 to 6, in which the continuous extension is concave.